EP0256465A1 - Controlled-deflection roll - Google Patents

Abstract

In the case of a deformation regulating roller (1), a roller shell (6) is rotatably mounted on a support (3) held in a rotationally fixed manner with the aid of a support device (8). The ends of the roll shell (6) are arranged on bearing bushes (15). At least one pin (19), which is offset by approximately 90 ° with respect to the support device (8), is provided for pivoting the bearing bush. This can reduce frictional forces to a practically insignificant level.

Description

The invention relates to a deformation control roller with a non-rotatably supported carrier, on which a rotating roller shell surrounding it is mounted with the aid of a support device, in particular having hydrostatic bearing elements, the ends of the roller shell being arranged via ring bearings on bearing bushes which are movable with respect to the carrier, but are secured against rotation by means of torque supports acting on the bearing bush.

Such deformation control rollers are suitable for numerous applications, be it as a pressure treatment roller, for example for calenders, smoothing units, press sections of paper, pulp and printing machines or rolling mills for steel, plastic and the like, be it as a deflection roller, as used for screens, textile webs and the like . Like. is used. With them, the shape of the roller can be changed as a whole or in zones by regulating or controlling the control signals to be supplied to the support device, for example the hydrostatic pressure.

A deformation control roller of this type is known from DE-OS 33 25 385. The torque arm consists of a roller rotatably mounted on the carrier via intermediate elements, which engages in a radial groove of the bearing bush. Two torque supports can also be arranged on both sides of the carrier. Here there are rollers and radial grooves in the effective plane, which is defined by the support device. The torque supports prevent the bearing bushes from rotating, so that the sealing rings which are in contact with them are not damaged, and at the same time allow a radial translational movement of the bearing bushes and of the roller shell located thereon.

Deformation regulating rollers are also known (DE-AS 22 54 392), in which the bearing bush has a window-like cutout with two parallel side walls which slide on parallel guide surfaces of the carrier. This is intended to guide the roller shell radially.

If, in the known cases, the roller shell is to be adjusted together with the bearing bush, for example by appropriate pressurization of the hydrostatic bearing elements, frictional forces between the bearing bush and the torque arm or the carrier have to be overcome. This is particularly serious when using the window-like cutout, because even with a slight tilting of the bearing bushing, jamming occurs at diagonally opposite locations on the contact surfaces and considerable breakaway forces have to be overcome. This risk is significantly reduced in the known torque supports, especially if they are designed as rollers. In the course of the operating time, however, because of the line contact, there can be considerable Hertzian pressures and thus flattening on the cylindrical surface, so that here too, friction forces can be overcome, albeit to a lesser extent. This affects sensitive control, especially if the frictional forces on the two bushings are different.

The invention has for its object to provide a deformation control roller of the type described in the introduction, in which frictional forces in the area of the torque arm are practically negligible.

This object is achieved in that the torque supports are offset by approximately 90 ° with respect to the support device and are each formed by at least one pin with an axis parallel to the longitudinal extension of the support for pivoting the bearing bush.

In this construction, the torque arm is offset transversely to the working plane and is designed as an eccentrically arranged pivot pin. As a result, there is no translational movement between the bearing bushes with the roller shell arranged thereon and the carrier, but a pivoting movement on a circular path. The relative movement of surfaces lying on top of each other is limited to the cylindrical surface of the pin and the associated bore. Because of the comparatively large contact surface, there is no fear of Hertzian pressure. Because of the cylindrical shape, jamming is also not possible. Because the pivot axis is at a distance from the effective plane, there is a leverage effect such that the frictional forces remaining in a cylindrical pivot bearing are effective in the effective plane with such a small proportion that they can be practically neglected.

Because no breakaway, clamping or frictional forces have to be overcome when adjusting the roller shell, and therefore no different forces have to be overcome at both ends of the roller shell, this results in an extremely precise and sensitive control.

It is particularly favorable if the pin is connected to the carrier in a rotationally fixed manner and the bearing bush can be pivoted about the pin. This has the advantage over the alternative of attaching the journal to the bearing bush that the distance between the cross-sectional center plane of the bushing and the journal sliding bearing is small. This reduces the risk of an undesired inclination of the axis of the bearing bush in the event of a transverse load, even if the pivot pin is only provided on one end face of the bearing bush.

In a preferred embodiment it is ensured that the pin protrudes from a step end face between the support section passing through the bearing bush and a thicker main part of the support. At this point, the carrier can have a considerably larger dimension than in the active plane because the surface does not have to be machined to receive the support device. A relatively large level can therefore be provided.

It is also possible for the pin to protrude from a sealing disk which is held on the carrier in a rotationally fixed manner and is arranged axially outside the ring bearing. It is only necessary to make the sealing washer so large that the pin is in the right place.

It is particularly advantageous to provide a journal in a coaxial arrangement on both sides of the roller bearing. This results in a particularly good storage, in which it is ensured that the central axis of the bearing bush remains parallel to its starting position with all loads.

This can be achieved in particular in that the bearing bush has two outer flanges, one of which is formed in one piece with it and the other is connected to it by fastening means. The two External flanges allow the pins to be arranged at a relatively large distance from the central axis of the bearing bush.

It is also favorable that the pin is movable on a path approximately parallel to the stroke direction of the support device. This design allows the swivel bearing to be used even on roller jackets with a long stroke. There is a double freedom of movement of the bearing bushing, so that it can be adjusted during operation so that its axis lies in or near the working plane.

One possibility is that the pin is carried by a sliding block, which is displaceable in a non-rotatably held groove on the support, which runs eccentrically approximately parallel to the stroke direction of the support device. For precise and sensitive control, it is sufficient if the low-friction swivel bearing is available in the working position of the roller shell. On the other hand, for large stroke movements, the swivel axis is shifted in the groove with the help of the sliding block. No jamming can occur here either, since the sliding block can adapt to the groove profile by rotating around the swivel axis.

From a design point of view, it is recommended that the groove for receiving the sliding block be provided in the step end face of the carrier and / or in the sealing washer. If you select a groove on both sides of the bearing, the sliding blocks move particularly securely.

Another preferred alternative consists in that the pin is carried by a lever which is pivotable about a support-fixed axis of a second pin diametrically opposite the pin. The swing around the second pin is just as low in friction as the pivoting around the first pin. The result is a kind of scissor movement that allows both a lifting movement and an alignment of the bearing bush on the working plane.

The lever is expediently arranged between an end face of the bearing bush and a step end face of the carrier and / or the end face of the sealing disk. The lever takes up little space there, but can still have a radially large width and therefore a corresponding stability.

The lever is particularly preferably formed by a ring which surrounds a carrier section passing through it with such play that the maximum ring stroke is less than the maximum bearing bush stroke. The ring shape leads to a particularly high stability of the lever. It also enables stroke limitation. This ensures, even under unfavorable circumstances, that with larger strokes both the ring and the bearing bush perform a pivoting movement, as is aimed at, so that the bearing bush axis remains in the area of the effective plane.

In a further embodiment, it is ensured that the bearing bush has an axially projecting edge on at least one side, which surrounds the ring with such play that the maximum relative stroke between the bearing bush and the ring is smaller than the maximum bearing bush stroke. This also results in a stroke limitation which ensures that both the ring and the bearing bush are pivoted on larger strokes.

It is favorable here that the sum of the maximum ring stroke and the maximum relative stroke is greater than the maximum Bearing stroke. In the rest position, when there is no hydrostatic pressure, the bearing bush is supported directly on the carrier.

A hydrostatic stabilizing device acting on the roll shell and / or on the bearing bush, with primary elements acting in the direction of the support device and secondary elements acting in the opposite direction, which due to their tensioning effect prevent at least an impermissibly large transverse displacement of the roll shell offers particular advantages. With the help of the primary and secondary elements, transverse forces acting on the roll shell can be absorbed. As a result, the pivot pin can be relieved of transverse forces, which in turn benefits the low-friction pivoting. In connection with the sliding block storage, the stabilizing elements lead to an automatic tracking of the sliding block. Because with increasing swivel angle, the transverse forces exerted by the stabilizing device on the roll shell increase until finally the sliding block is completely or almost relieved of transverse forces and therefore adjusts in the groove.

In the simplest case, the hydrostatic bearing elements of the support device serve as primary elements. They can have such a dimension in the circumferential direction that they are suitable for absorbing transverse forces. It is particularly favorable if they are loaded by at least two pressure transducers offset in the circumferential direction, each consisting of piston and cylinder. Such bearing elements are known for example from DE-PS 30 22 491.

In general, it is sufficient if the primary elements can absorb transverse forces, while the secondary elements only serve to achieve the desired tensioning effect. But there is also the possibility that the Secondary elements are formed by hydrostatic bearing elements acting on the roll shell in the opposite direction. Like the primary elements, these are able to absorb lateral forces.

An alternative is that a piston-cylinder arrangement is arranged at least as a secondary element between the bearing bush and the carrier section passing through it. This construction has the advantage that there is no relative rotation between the bearing bush and the primary or secondary element. The bearing bush can even be connected to parts of the piston-cylinder arrangement.

In particular, a piston fixedly attached to the bearing bush can engage with great play in a cylinder bore in the carrier section. The large game ensures that the pivoting movement of the bearing bush is not hindered by a guide of the piston in the cylinder bore.

In a further embodiment of the invention, it is ensured that sliding elements are provided on at least one end face of the bearing bush, the total area of which is considerably smaller than the end face area. In this way, the contact surface with the neighboring part, for example the step of the carrier and / or the sealing washer, is reduced, which likewise leads to a reduction in the frictional force to be overcome when the bearing bush is adjusted. In addition, the sliding elements can consist of a material with improved sliding properties, for example bronze. In addition, the finely machined surfaces on sliding elements and neighboring parts are smaller, which saves costs.

In particular, a sliding element can be formed by a ring surrounding the pin. You then do not need any special fasteners.

If possible, one end face should be assigned three sliding elements offset by approximately 120 ° from one another. This results in a three-point support and therefore a high degree of stability.

The sliding elements provided between the bearing bush and the sealing disk are preferably arranged within the sealing ring located between these parts. The sliding elements can therefore still be lubricated with the oil present in the interior of the roll shell. In addition, the sliding elements ensure that the sealing ring is not loaded, but can be designed solely with regard to its sealing function.

• Fig. 1 einen Längsschnitt durch den Endbereich einer erfindungsgemäßen Deformationsregelwalze gemäß der Linie A-A in Fig. 2,
• Fig. 2 einen Querschnitt längs der Linie B-B in Fig. 1,
• Fig. 3 einen Schnitt längs der Linie C-C in Fig. 1,
• Fig. 4 einen Längsschnitt durch den Endbereich einer abgewandelten Ausführungsform,
• Fig. 5 einen Längsschnitt durch den Endbereich einer weiteren Ausführungsform,
• Fig. 6 einen Querschnitt längs der Linie D-D in Fig. 5,
• Fig. 7 einen Längsschnitt durch den Endbereich einer vierten Ausführungsform,
• Fig. 8 einen Querschnitt längs der Linie E-E in Fig. 7,
• Fig. 9 einen Längsschnitt durch den Endbereich einer fünften Ausführungsform,
• Fig. 10 einen Querschnitt längs der Linie F-F der Fig. 10,
• Fig. 11 den gleichen Querschnitt bei abgesenkter Lager­buchse und
• Fig. 12 einen Querschnitt längs der Linie G-G der Fig. 9 bei abgesenkter Lagerbuchse.

The invention is explained in more detail below with reference to preferred exemplary embodiments illustrated in the drawing. Show it:

• 1 shows a longitudinal section through the end region of a deformation regulating roller according to the invention along the line AA in FIG. 2,
• 2 shows a cross section along the line BB in FIG. 1,
• 3 shows a section along the line CC in FIG. 1,
• 4 shows a longitudinal section through the end region of a modified embodiment,
• 5 shows a longitudinal section through the end region of a further embodiment,
• 6 shows a cross section along the line DD in FIG. 5,
• 7 shows a longitudinal section through the end region of a fourth embodiment,
• 8 shows a cross section along the line EE in FIG. 7,
• 9 shows a longitudinal section through the end region of a fifth embodiment,
• 10 is a cross section along the line FF of FIG. 10,
• 11 shows the same cross section with the bearing bush lowered and
• Fig. 12 is a cross section along the line GG of FIG. 9 with the bearing bush lowered.

In the embodiment of FIGS. 1 to 3, the deformation regulating roller 1, which can cooperate with a counter roller 2, has a carrier 3, which is held in a stand 5 in a rotationally fixed manner at both ends via a pivot bearing 4. A roller jacket 6 rotatably surrounds the carrier 3 and is supported on it by means of a support device 8. This support device has axially adjacent bearing elements 9, which are loaded by two circumferentially offset pressure transmitters 10 and 11, each consisting of a piston on the carrier 3 and a cylinder bore in the bearing element 9, and are provided with pressure pockets 12 and 13 for hydrostatic jacket storage . For further details of this hydrostatic bearing, reference is made to DE-PS 30 22 491.

Furthermore, the ends of the roller shell 6 are each supported by a roller bearing 14 on a bearing bush 15, the cylindrical central opening 16 surrounds a cylindrical support section 17 with a reduced diameter. The carrier 3 therefore has a step 18 at the transition point. This step has a greater radial width in the section plane AA of FIG. 2 than in the area the effective plane H determined by the gap between the rollers 1 and 2, because the carrier 3 has a flattened portion for attaching the support device 8. In a bore of this stage, a pin 19 is fastened and offset by approximately 90 ° relative to the support device 8 and secured by an adjusting screw 20. This pin 19 engages with sliding play in a bore 21 of the bearing bush 15. The bore is housed in an outer flange 22 which is located laterally next to the roller bearing 14.

As a result, as shown in FIG. 2, the bearing bush 15 can be pivoted about the pin 19, namely between a lower position in which the bearing bush 15 strikes the support section 17 at the top and an upper position in which the bearing bush strikes the top of the support section. Here, all parts of the bearing bush 15 move on circular arc sections. A circle K with the radius r is indicated in FIG. 2, on which a point P located in the plane of symmetry on the inner circumference of the bearing bush 15 moves over a certain section.

Since the bearing bush 15 only pivots about the cylindrical pin 19, no jamming can occur during this movement. Any remaining frictional force on the cylindrical pin surface is negligible because it only has a fraction of its value due to the leverage in the effective plane E. The pin 19 forms a torque arm, which prevents the bearing bush 15 from rotating. As a result, there is only a slight relative movement between the bearing bush 15 and a sealing ring 24, which is attached to a sealing disk 23 held in a rotationally fixed manner on the carrier 3.

The bearing bush 15 has two outer flanges. The outer flange 22 is formed in one piece with the bearing bush. The outer flange 25 is connected to it by fastening means, not shown. On the end faces of the bearing bush 15 formed by the outer flanges, three sliding elements made of a low-friction material, such as bronze, offset by 120 ° relative to one another are provided. Fig. 3 shows the three sliding elements 26, 27 and 28 between the outer flange 22 and the step 18 of the carrier 3. The sliding element 26 is placed as a ring around the pin 19.

The sliding elements 27 and 28 are attached to the outer flange 22 as disks. On the outer flange 25, three disk-shaped sliding elements are attached in a similar distribution within the circumference of the seal 24, of which the sliding elements 29 and 30 can be seen in FIG. 1. At the step 18 and the sealing disk 23, only the surfaces opposite the sliding elements need to be finely machined.

In Fig. 4, the same reference numerals as in Figs. 1 to 3 are used for the same parts. Corresponding parts are given reference numbers increased by 100. The bearing bush 115 is pivotally mounted on two coaxial pins 119 and 119a. The pin 119 is fastened in the carrier by means of an adjusting screw 120. The pin 119a is fastened to the sealing disk 123 by means of an adjusting screw 120a, which is connected to the carrier 3 in a rotationally fixed manner. The pin 119a engages in a bore 121a in an outer flange 125 of the bearing bush 115, which is located axially outside of the rolling bearing 14.

In this construction, since the bearing bush 115 is pivotally mounted on both sides of the roller bearing 114, the axis of this bearing bush remains even under extreme loads parallel to their rest position. The pin cross sections can be kept smaller because the forces to be absorbed are distributed over two pins.

The sliding elements correspond to those of Figures 1 to 3; only the sliding element 129 is designed as a ring surrounding the pin 119a.

The embodiment of FIGS. 5 and 6 corresponds to that of FIGS. 1 to 3. The same reference numerals are used for corresponding parts. In the case of modified parts, the reference number is increased by 200. It is different that the pin 219 is rotatably held in a sliding block 31 which is displaceable in a groove 32 on the shoulder 218 of the carrier 203. The groove extends eccentrically approximately parallel to the stroke direction of the support device 8 or the effective plane H.

The bearing elements 9 form primary elements of a hydrostatic stabilization device, which also includes a secondary element 33 in each bearing bush 215, which acts in the opposite direction. It consists of a piston 34 attached to the bearing bush 215 and a cylinder bore 35 in the carrier section 217. The cylinder bore 35 can be supplied with pressure fluid with adjustable or controllable pressure via a line 36. The same applies to a corresponding primary element 37, which can also be located in the area of the bearing bush 215. The piston 34 has a large play in the cylinder bore 35 so that the pivoting movement of the bearing bush 215 about the pin 219 can take place without hindrance. It is also possible to shut off the displacements of the primary and secondary elements 33, 37 with the aid of check valves, so that the ends of the roll shell 6 can be held in selectable bearings.

In the working position, the bearing bush 215 pivots in the same way around the pin 219, as is the case with a fixed mounting of this pin. However, if the roller jacket is adjusted by a larger stroke by the support device 8, the bearing bush takes the slide block 31 with it via the pin 219. When the roller jacket 6 tries to move in the transverse direction, the bearing elements 9 exert corresponding counter-transverse forces, whereby they are supported on the pistons fixed to the carrier. These transverse forces can be increased by simultaneously increasing the pressures supplied to the primary elements 9 and the secondary elements 33. As a result, the transverse force acting on the pin 219 or on the sliding block 31 is limited. As the swivel angle increases, the transverse force on the pin decreases to almost zero, whereupon the sliding block 31 can move freely in the groove 32.

The embodiment of FIGS. 7 and 8 corresponds to that of FIG. 4. Therefore, the same reference numerals are used for the same parts and reference numerals beginning with 300 for modified parts. The essential difference is that the hydrostatic stabilization device has the bearing elements 9 as primary elements and bearing elements 38 arranged as secondary elements on the opposite side. In addition, two pins 319 and 319a are again provided on both sides of the roller bearing 14. They are each locked in a sliding block 331 or 331a. The sliding block 331 is displaceable in a groove 332 in the carrier 303, the sliding block 331a in a groove 332a in the sealing disk 323. The two grooves have the same course as the groove 332 in FIGS. 5 and 6. The function of this construction also corresponds 5 and 6.

In the embodiment of FIGS. 9 to 12, the same reference numerals are used for identical parts and for modified parts 400 reference numerals beginning. In this construction, the pins 419 and 419a are mounted in bearing sleeves 433, 433a of the bearing bush 415. They are firmly connected to a ring 434, 434a. The rings form levers which can be pivoted about carrier-fixed axes by second pins 435, 435a. For this purpose, the pin 435 fastened in the ring 434 engages in a bearing sleeve 436 on the step end face 418 of the carrier 403. And the pin 435a fastened on the ring 434a engages in a bearing sleeve 436a in the sealing disk 423 fastened non-rotatably on the carrier 403. The ring 434 is located between the step end face 418 of the carrier and an end face 437 of the bearing bush 415. The ring 434a is located between an end face 438 of the bearing bush 415 and an end face 439 of the sealing disk 423. Above the end face 437 there is an annular edge 440 of the bearing bush 415 axially about. An annular edge 441, which carries the seal 424, projects axially beyond the end face 439.

Between the ring 434 and the carrier section 17 passing through it there is a game x 1, which corresponds to a maximum ring stroke, between the ring 434 and the edge 440, a game x 2, which corresponds to a maximum relative stroke, and between the bearing bush 415 and the carrier section 17, a game x₃, which corresponds to a maximum bushing stroke. x₃ is less than the sum of x₁ + x₂, but greater than x₁ or x₂ alone. The result of this is that in the lower end position of the roll shell 6, the ring 434 rests on the carrier section 17 (FIG. 11) and the bearing bush 415 on the carrier section 17 (FIG. 12), but still between the edge 440 and the ring 434 a small space remains (Fig. 11).

10 shows the middle position in which the bearing bush 415 concentrically surrounds the carrier section 17. The axes M₁ of the bearing bush 415 and the axis M₂ of the support section 17 coincide.

In Fig. 11 it is illustrated how the axis M₁ of the bearing bush relative to the axis M₂ of the support section has been shifted downwards by a double pivoting movement. The connecting line between pins 419 and 435 has been rotated by pivoting the ring 434 about the pin 435 by the angle α. The connecting line between the pin 419 and the axis M₁ of the bearing bush 415 has been rotated by pivoting about the pin 419 by the angle β. Because of this double pivoting, the deviation of the axis M₁ from the effective plane H is minimal.

There can be deviations from the illustrated embodiments in many ways without departing from the basic idea of the invention. The bearing elements 9 can have a circular bearing surface and can be loaded by only one pressure sensor. A continuous chamber filled with hydraulic fluid can also be used as a support device. Various known principles are available for the control. The pin 19 can also be attached to an annular disk fixedly attached to the support. In this case, the carrier can have the same cross section throughout. It is also possible to lock the pin in the bearing bush and to use the hole in the carrier, in the sealing washer, in the sliding block or in the ring as a pivot bearing. 5 to 8, the sliding block can also be equipped with hydrostatic bearing pockets on both sides, to which pressure fluid is supplied, which further reduces the risk of friction during sliding block displacement.

Claims (23)

1. Deformation regulating roller with a non-rotatably supported carrier, on which a rotating roller shell surrounding it is mounted with the aid of a support device, in particular with hydrostatic bearing elements, the ends of the roller shell being arranged via ring bearings on bearing bushes which are movable relative to the carrier, but with the aid of the torque supports engaging the bearing bush are secured against rotation, characterized in that the torque supports are offset by approximately 90 ° with respect to the support device (8) and each by at least one pin (19; 119, 119a; 219; 319, 319a; 419, 419a) are formed with an axis parallel to the longitudinal extension of the support for pivoting the bearing bush (15; 115; 215; 415). 2. Deformation control roller according to claim 1, characterized in that the pin (19; 119, 119a; 219; 319, 319a; 419, 419a) with the carrier (3; 203; 303; 403) rotatably connected and the bearing bush (15; 115; 215) is pivotable about the pin. 3. Deformation control roller according to claim 1 or 2, characterized in that the pin (19; 119; 219; 319; 419) of a step end face (18; 218; 318; 418) between which the bearing bush (15; 115; 215 ; 415) penetrating carrier section (17; 217; 417) and a thicker main part of the carrier (3; 203; 303; 403) protrudes. 4. Deformation regulating roller according to one of claims 1 to 3, characterized in that the pin (119a; 319a; 419a) of a on the carrier (3; 203; 303) rotatably held, axially outside of the ring bearing (14) arranged sealing washer (123, 323; 423) protrudes. 5. Deformation control roller according to one of claims 1 to 4, characterized in that on each side of the ring bearing (14) a pin (119, 119a; 319, 319a; 419, 419a) is provided in a coaxial arrangement. 6. Deformation control roller according to one of claims 1 to 5, characterized in that the bearing bush (15; 115; 415) has two outer flanges (22, 25; 125; 422, 425), one of which is formed in one piece with it and the other connected to it by fasteners. 7. Deformation regulating roller according to one of claims 1 to 6, characterized in that the pin (219; 319, 319a; 419, 419a) is movable on a path approximately parallel to the stroke direction of the support device. 8. Deformation regulating roller according to claim 7, characterized in that the pin (219; 319, 319a) is carried by a sliding block (31; 331, 331a) which is held in a rotationally fixed manner on the carrier (203; 303) groove (32; 332, 332a) is displaceable, which runs approximately parallel to the stroke direction of the support device (8). 9. Deformation regulating roller according to claim 8, characterized in that the groove (32; 332, 332a) for receiving the sliding block (31; 331, 331a) in the step end face of the carrier (203; 303 and / or in the sealing disc (323 ) is provided. 10. Deformation regulating roller according to claim 7, characterized in that the pin (419, 419a) is carried by a lever (434, 434a) which is pivotable about a diametrically opposite pin-fixed axis of a second pin (435, 435a). 11. Deformation regulating roller according to claim 10, characterized in that the lever (435, 435a) between an end face (437; 438) of the bearing bush (415) and a step end face (418) of the carrier (403) and / or the end face ( 439) of the sealing washer (423) is arranged. 12. Deformation regulating roller according to claim 10 or 11, characterized in that the lever is formed by a ring (434, 434a) which surrounds a carrier section (17) passing through it with such play (x₁) that the maximum ring stroke is smaller than that maximum bushing stroke is. 13. Deformation control roller according to claim 12, characterized in that the bearing bush (415) has at least on one side an axially projecting edge (440) which surrounds the ring (434) with such play (x₂) that the maximum relative stroke between Bearing bush and ring is smaller than the maximum bearing bush stroke. 14. Deformation control roller according to claims 12 and 13, characterized in that the sum of the maximum ring stroke and the maximum relative stroke is greater than the maximum bearing stroke. 15. Deformation regulating roller according to one of claims 1 to 14, characterized by a hydrostatic stabilizing device acting on the roll shell and / or on the bearing bushing with primary elements (8; 37) acting in the direction of the supporting device (9) and secondary elements (33; 38) acting in the opposite direction ), which at least prevent an impermissibly large transverse displacement of the roller shell due to their tensioning effect. 16. Deformation control roller according to claim 15, characterized in that the hydrostatic bearing elements (9) of the support device (8) serve as primary elements. 17. Deformation regulating roller according to claim 15 or 16, characterized in that the secondary elements are formed by hydrostatic bearing elements (38) acting on the roller shell in the opposite direction. 18. Deformation regulating roller according to one of claims 15 to 17, characterized in that a piston-cylinder arrangement is arranged at least as a secondary element (33) between the bearing bush (215) and the carrier section (217) penetrating it. 19. Deformation regulating roller according to claim 18, characterized in that a piston (34) firmly attached to the bearing bush (215) engages with a large clearance in a cylinder bore (35) in the carrier section (217). 20. Deformation regulating roller according to one of claims 1 to 19, characterized in that on at least one end face of the bearing bush (15; 115; 215) sliding elements (26 to 30) are provided, the total area of which is considerably smaller than the end face. 21. Deformation control roller according to claim 20, characterized in that a sliding element (26; 129) is formed by a ring surrounding the pin (19; 119, 119a). 22. Deformation control roller according to claim 20 or 21, characterized in that one end face three sliding elements (26, 27, 28) offset from one another by approximately 120 ° are assigned. 23. Deformation regulating roller according to one of claims 20 to 22, characterized in that the sliding elements (29, 30; 129, 130) provided between the bearing bush (15; 115) and the sealing disc (23; 123) within the sealing ring (24 ) are arranged.

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